Hydraulic power transmission mechanism



April 23, 1935.I A w. CHAMBERLAIN ET AL 1,998,922

HYDRAULIC POWER TRANSMISSION MCHANISM Filed June 7, 1952 6 Sheets-Sheet 1 April 23,1935.

A. w. CHAMBERLAIN l-:T AL

` HYDRAULIC POWER TRANSMISSION MEC'IANISM Filed Juhe v, 1952 6 Sheets Howard Fmnuswlq -SheeiuI 2 NvEN-ron April 23 1935 l A. w; CHAMBERLAIN E-r Al. 1,998,922

HYDRAULIC POWER TRANSMISSION MECHANISM 6 Sheets-Sheet 5 Filed June '7, 1932 F'lc 'I Mq Hmnkef Chambarmm tewfw Attornny',

cs. A

A. W. CHAMBERLAIN ET AL HYDRAULIC POWER TRANSMISSION MECHANISM Filed June '7, 1932 6 Sheets-Sheet 4 vvim-row! y April 23, 1935. A. w. CHAMBERLAIN E-r AL 1,998,922 g HYDRAULIC POWER TRANSMISSION MECHANISM Filed June 7, 1932 6 sheets-sheet 5 WIHI'am Chambedorg wKeY Chamberlm'n o foflnswlwhr Chumbejlam wor RNVENTORS "ULL mamey.

April 23, 1935,

A. w. c|-|AMBER| A|N ET A1. 1,998,922` HYDRAULIC POWER TRANSMISSION MECHANISM Filed June '7, 1932 l H wkr Chamberlcun.' 30:12:11 nnoswdzrChumnrlw INVEN-rong B! M Attorney.

Patented pr 23,

UNITE STATES 1,998,922 HYDRAULIC rowEa 'raANsmssron Mecnms Albert William Chamberlain, Ahn

Howard Francis Winter Chamberlain, and

Chamberlain, Brunswick,

1932, Serial No. 615,@6@

Application kJune 7,

In Australia claim.

This invention relates to hydraulic power transmission mechanism which combines the functions of al clutch and change speed gear and which is particularly suitable for use in automobiles but 5 is applicable to -other purposes.

Transmission mechanis vention a driving member and a m according to this inis characterized by the combination with driven member oi two units each having a central gear and a plurality of planetary pinions, adapted to be connected by a body of liquid and at the so arranged that when liquid delivery side of one of the units is under pressure motion is transmitted from the driving member to the driven member increased torque at reduced speeds.

with proportionate Features of the invention include means whereby the effective relative capacity of the units may be varied to control the cause transmission tion at variable speeds; means hydraulic pressure to of motion in the same directo stop the flow of liquid between the said units so as to cause the driven member to be rotated at the same speed as the driving member; and means whereby the relative capacity of the units may be varied so as to cause the driven member to be rotated in the opposite direction to the duced speeds.

Other features of this whereby the driving member at reinvention include means pressure of liquid on movable members is balanced to facilitate control thereof;

means whereby pressure to each planetary pinion is balanced relatively to relieve load on its bearing; and means to provide an unrestricted escape for liquid at the ends of the teeth in addition to means for ingress the faces of the teeth.

and egress of liquid on A further feature of this invention is the combination with the said units of a revolvable liquid container, a fixed structure,

a one-way engaging brake, and brake mechanism whereby the said brake may be locked.

Another feature of this invention is liquid ow control valve mechanism which under certain conditions allows the driven member to over-run the driving member.

Still further features of means to maintain reservoirs with liquid; means to prevent the invention include completely filled accumulation of air and bubbles in said reservoirs; and means to compensate pulsations and shocks to hammer.

Any suitable liquid liquid is anoil the reasonably constant at va this description the term liquids.

-The above and prevent is usable but the preferred viscosity of which remains rying temperatures. In oil includes all suitable other features of the invention as embodied in transmission mechanism suitable for automobiles will now be fully described with Hawker Victoria, Australia June 11, 1931 (Cl. dil-53) reference to the accompanying drawings which are to sonie extent diagraatic. In the drawings:

Fig. 1 is a. longitudinal vertical section of an arrangement in which one gear unit is adapted to function both as a pump and as a motor and the other unit is of variable capacity and is adapted to function as a liquid trol means or as a pump to cause transmitted in the reverse direction, being shown in the latter position.

Fig. 2 is a plan of flow and pressure conmotion to be the parts parts in Figure l but with the outer casing and parts adacent to the driving and driven members in central section.

Fig. 3 is a transverse section mainly on line 3 3 of Figure 1 but with some parts broken away.

Fig. 4 is a perspective view showing some of the parts in Figure 1 diagrammatically.

Figs. 5-9 aretransverse sections showing some of the parts on respective lines 5 5, 6 5, f l,

8 3, and 9 9 of Figure l. As the parts on these section lines are symmetrical relatively to the axis of rotation the quadrant shown is typical of the whole section.

' Fig. 10 is a similar view to Figure 9 but with the parts in a different position, the centre gear having been moved beyond the line on which the section is taken.

Figs. 11-16 show the control valve in Figure l and associated spur gear pump mechanism in positions which correspond respectively with neutral, intermediate speed, top speed, top speed top speed.

with valve in over-running position, without over-run and reverse.

Fig. 17 is a longitudinal vertical section of a modified arrangement in which one unit is unit adapted to function as a pump and the other as a motor.

Fig-18 is a detail sectional view showing means to balance pressure relatively to a planetary pin- Y ion. f

Fig. 19 vto provide an unrestricted escape for liquid the ends of the teeth of a gear unit.

1 to 16 and particularly are supported in bearings support, for example is a detail sectional View showing means ber. Shaft 2| is connected by a coupling 25 to one end a cylindrical casing shaft 22. ported co-axially with 28 carried by coupling 25.

One .gear unit comprises a gear shaft 22 and a plurality of planetary pinions 26 the other end of which is supported by -a ball bearing 21 relatively to The adjacent end of shaft 22 is supshaft 2l by a ball bearing (four for example) each of which is freely rotat able on an axle 3|)a fixed to casing 26. The other gear unit comprises a gear 32 fixed to a slidable sleeve 34 and a plurality of planetary pinions 33, each. of which is freely rotatable on an axle 339L fixed to casing 26. Sleeve 34 carries bearings 21 and as hereinafter described is arranged so that it is normally free to rotate in a forward direction but is held against movement in the reverse direction.

'I'he output of a gear pump varies with'the relative angular position of the meshing teeth, resulting in a uctuating output and hammer, and to minimize this defect the-number of teeth on each gear wheel 29 and- 32 is such that it is not divisible by the number of pinions in the respective series associated with it. 35 is an oil reservoir between casing partitions 26b and 266. Associated with each planetary pinion 30 is an inlet port 36 and 'an outlet passage 36S.

Ports 36 are open to reservoir 35 and passages 36a communicate with part 31'Il of a reservoir 31 from part 31b of which extend passages 38 one of which is associated with the inlet side of each planetary pinion 33 from which is an outlet 39 leading to reservoir 35. The said ports and passages are so arranged that resistance to ingress and egress of liquid to and from the faces of the teeth of each unit is minimized, and in addition, to provide an unrestricted escape for liquid at the ends of the teeth suitably located clearances 36c are provided (see Figure 19) To balance pressure to relieve load on the bearings of the planetary pinions each outlet is connected by a passage 36l to a balance port 36e and in addition there is between the pressure points a' clearance 36f (see Figure 18) which is connected to reservoir in any suitable manner.

Each reservoir has an oil supply port 40 provided with a non-return valve 4|l"l and connected by a pipe 4|, passages 42 and a pipe 43 to a pump 44 at the base' of casing 24. Pump 44 is actuated by a shaft 45 which is driven by chain and sprocket gear 46, 46, an over-running clutch 46b being provided in the driven sprocket of each gear.

Any suitable number of outlets 41 (one shown) each having a valve 41 extend from suitable positions near the centre of the reservoirs for escape of air bubbles and oil foam. One outlet 41 from a passage 16 hereinafter referred to is suillcient in some cases.

415' is a spring loaded vplunger which is in contact with oil under pressure and which is adapted to compensate pulsationsand shocks. This plunger is suitably located as in an open ended passage 41X.

Fixed to sleeve 34 is the inner-member 48 of an v over-running brake. The outer member 48L of this brake carries diametral projections 49, each of which engages a cam slot 50 in a disc 5| xed on a cranked rock shaft 52 which is supported in bearings on the outer fixed casing 24 and one end of which projects to carry a control lever 52a. 'When discs 5| are rotated by operation of lever 52a the co-action of projections 49 with theirv respective slots 50 causes sliding movement to be transmitted through projections 49, brake members 48a and 48 and sleeve 34 to gear 32 to vary the capacity of unit 32-33. Sleeve 34 is supported relatively to a slidable sleeve 53 by 1a radial ball bearing 54 and a combined radial and thrust bearing 55 so that although sleeve 34 is freely rotatable, longitudinal movement is transmitted through bearing 55 to sleeve 53.

On an extension 56 of sleeve 53 are projections surrounds the louter face of gear wheel 32 cooperate to balance hydraulic pressures relatively to gear 32 to facilitate free longitudinal movement;

To hold member 48'- against rotation but allow longitudinal movement each member 49 extends beyond its disc 5| and carries a roller 6| located in a runway 62 on casing 24. Rollers 4|!b between brake members 48, 48a allow the inner member to rotate freely in one direction but prevent relative movement in the opposite direction. This arrangement permits gear 32 to over-run.

Brake member 48 is connected by anchor plates 63b to the band 631i of a brake drum 63. An extension on a plate 63b carries a roller 63c which is in a converging slot 63d so that when gear 32 is moved'to cause reverse motion to be transmitted the brake 63a is operated to hold brake member 48.

64 is a slidable valve control sleeve which is adapted to be moved longitudinally by a member 65 slidably housed in a recess in shaft 22. The connection between sleeve 64 and member 65 is such that sleeve 64 may rotate freely. This connection is shown diagrammatically in Figures 1 and l1 to 16. The outer end of member 65 is connected through collar 66 to a non-rotatable shoe 66a having projections 61 each of which en-V rotation of discs 5| causes co-operating differential movement to be imparted to the gear 32 and to the sleeve 64.

A sleeve 68 which extends from casing 26 surrounds sleeve 64 and another sleeve 69 which is about sleeve 68 is connected to sleeve 64 b y a pin 10 which is slidable in aslot in sleeve 68. At opposite ends of sleeve 69 are valve rings 1| and 12 respectively, between which is a movable valve ringv 13 which is normally pressed against a stop 14 by a spring 15. There is an oil passage 69a to an annular chamber 69b so that the hydraulic pressure is balanced relatively to sleeve 69.

Members 1|, 12 and 13 are adapted to co-operate with an annular passage 16 between reservoir 35 and reservoir part 31.a while member 12 -is also adapted to cooperate with an annular port 11 connecting reservoir parts 31 and 31h. l In operation when shaft 2| is revolving and annular passage 16 and annular port 11 are open, oil will flow (see Figure 4) from the reservoir 35 through ports 36, unit 29-30, passages 36a, reservoir 31, passages 38, unit 3233 and ports 39 back to reservoir 35. When gear 32 is set so that the capacity of unit 32-33 is equal to the capacity of unit 32-33 is equal to the capacity of unit 29--39 (see Figure 11), lplanetary pinions 30 and 33 will revolve about their respective gear wheels ,and oil will flow freely. Under these conditions gear 29 remains stationary and no motion is transmitted to shaft 22. With the parts in this position, if the engine is stopped, gear 29 and shaft 22 are free to turn in either direction; this would permit a vehicle fitted with the invention to be moved by external power.

If control lever 52B be operated so as to move gear 32 to reduce the capacity of unit' 32-33 and F to move valve parts so that member 13 closes passage 16 (Figure 12,) the full volume of oil which would be delivered by unit 29-30 if gear 23, were stationary could not pass through unit 32-33 and the oil in passages l36, reservoir 31 and passages 38 will be under pressure which reacts causing gear 29 to revolve in the same direction as the planetary pinions 30, asing v26 and the driving shaft 2|.

Motion in reduced ratio with proportionate increased torque is thus transmitted to the driven shaft 22. As the capacity of unit 32-33 is further decreased the speed of the driven shaft will increase in infinitely vvariable ratio within the limit of movement of gear 32. The shape of cam groove 50 is such that after the capacity of unit 32-33 has been reduced to the minimum to attain the highest reduced speed, further move- -ment of rdiscs 5| will not cause movement of gear 32 but such further movement by reason of the shape of cam groove 50 is transmitted to the valve sleeve 65 so that member 12 closes annular port 11, the parts then being in the position shown in Figure 13. A

Closure of port 'l1v stops the oil ow and locks pinions 3G relatively to gear-29V causing shaft 22 to be revolved at the same speed'as shaft 2 I. Assuming now that with the parts in this position the engine be stopped as when an automobile is coasting or that conditions are such that the shaft 22 tends to travel faster than shaft 2|, then gear 29 must be free to over-run. As soon as gear 29 tends to over-run pressure is exerted on the oil in reservoir and valve member 13 moves against the pressure of spring 15 to the position in Figure 14; Oil may then circulate freely from reservoir 35 through passage 16, reservoir part 31a, passages 36, unit 29-30 and ports 36 back .to reservoir 35. When it is not desirable to permitgear 29 to overr-,run the valve parts are moved until member 12 closes port 16 as shown in Figure 15. I

It will be clear that movement of control lever 52a in opposite direction will causemotion to be transmitted at reducing speeds until the neutral position is again reached. If gear wheel A32 is moved from neutral position (Figure 11) vfurther into mesh with its pinions the capacity of unit 32-33 is increased so that it is greater than the capacity of unit 29-30 and at the same .time valve member 1| is moved to close passage 16. Simultaneously, band 63*a is operated to hold brake member 48 as before described. As pinions 33 rotate around their gtar 32 at the same speed as pinions 30'around gear 29 and as the passage 16 is closed by member 1|, liquid in reservoir 35 which is then at the delivery side of the unit 32-33 will be under pressure, andr brake member 48 being held, unit 29-30 will operate asia motor and drive shaft 22 in the reverse direction.

In the arrangment shown in Figure 17 unit 29-30 functions as a pump and unit 32-33 funcf tionsv as a `motor to transmit motion to l shaft 2,2 at a speedfwhichis controlled by the quantity of oil under pressure admitted to unit 32-33 and the distributionof such oil to its planetary gears. In this case gear wheels 29 and 32 are both fixed to shaft 22,` the axles 30a of pinions 33 are carried by a casing`2|x fixed to the end 'of shaft 2| and the axles 33a of pinions 33 are carriedby a freely revolvable casing 265' which carries the inner member 48X of an over-running brake the outer member' 481' of which is fixed to casing 24.

lIn this construction shaft 22 is hollow and contains a slidable valve 69x which has an annular valve passage 69y and which is connected by spider 65y to a member 65X which is in turn con,- nected to a collar 66 by a pin 66x which is slidable ina slot 66)' in shaft 22. The non-rotatable shoe 66 of"collar 66 is connected to a control lever The interior of casing 26x constitutes a reservoir 35x having inlet ports 36 associated with unit 29-30 and which is connected to the interior of shaft 22 by ports 35S'. of unit 29-30 terminates in an annular passage 36x which is connected to the interior of shaft 22 by ports 365.

Another series of ports 38y connect the interior of shaft 22 to a plurality of annular passages 38x from which extend respective passages 38 associated with the inlets of unit 32--33 the outlets 39 of which are connected by an annular passage 39X and ports 39y with the interior of shaft 22.

The position illustrated corresponds with neutral the valve being located so that ports 38y are closed and ports 3Ey and 35y are connected through shaft 22. Oil willthus circulate freely passing from reservoir 35x through ports 36, unit 29-30 passages 36a and 36x, ports 36Y, shaft 22 and ports 35y back to reservoir 35X. Unit 32-33 is inoperative and no motion is transmitted to shaft 22, but brake 48X-485' allows this shaft to be rotated forwardly if the vehicle is moved by independent power.

For transmission of low speed the valve 69x is moved so that its passage 69y connects one annular series of ports 36y to all ports 38V. Thus the outlet relatively to one pinion of unit 29-30 is distributed relatively to all the pinions of unit 32-33. The torque reaction is taken by the overrunning brake 48"--48y and gear 32 and shaft 22 rotate slowly. In this position the output of the other pinions 30 of the pump unit 29-30 is bypassed through passages 36X, ports 365', shaft 22 and ports 355' back to reservoir 35X.

For higher speeds the valve is adjusted first to connect moreof the ports 36y to all the ports 36y and for still higher speeds the ports 385' are closed in succession.

When all ports. 38Y are closed and all ports 36y are connected to valve passage 69Y the oil flow is stopped thus locking unit 29-30 and causing shaft 22 to be rotated at the same speed as shaft 2|. Supply of oil to unit 32-33 being cut off the overrunning brake 48X-lily allows this unit and its associated casing 26Y to rotate with shaft 22.

We claim:

1.*In hydraulic power transmission mechanism, a revolvable casing, a-liquid circulation systern in said casing, a gear pump unit of fixed capacity and a gear pump unit of variable capacity eachcomprising a centre gear and a plurality of planetary pinions disposed in said system, means to rotatively support the .planetary pinions relatively to the casing, a driving member to rotate said casing, a driven member connected to the centre gear of the fixed capacity unit, a one-way engaging brake mechanism whereby the centre Each outlet passage.36a

gear of the variable capacity unit is held against capacity unit whereby motion is transmitted to the driven member in the reverse direction relatively to the driving member.

2. Hydraulic power transmission mechanism, as claimed in claim 1 with a duct connecting the fluid circulation system and the input of the fixed capacity unit and means to close said duct when the capacity oi' the variable capacity unit is less than that of the ilxed capacity unit.

3.. Hydraulic power transmission mechanism, as claimed in claim 1, with a duct connecting the fluid circulation system and the input of the fixed capacity unit and means whereby when the variable capacity unit has attained `its minimum capacity position the ilow of liquid through the circulation system is stopped and the said duct is closed.

4. Hydraulic power transmission mechanism, as claimed in claim 1, with a duct connecting the fluid circulation system and input' of the ilxed capacity unit, means whereby when the variable capacity unit has attained its minimum capacity position the flow of liquid through the circulation lsystem is stopped and means whereby the said duct is also closed in such manner that when pressure is exerted on the liquid at the input side of the fixed capacity unit the duct opens, short circuiting the xed capacity unit so that the centre gear of the last mentioned unit and the driven member may over-run.

5. Hydraulic power transmission mechanism, as claimed in claim 1, with a duct connecting the fluid circulation system and the input of the ilxed capacity unit, means whereby when the variable capacity unit has attained itsminimum capacity position the ow of liquid through the circulation system is stopped and means whereby the said duct is closed, the last mentioned means being resiliently held in operative position so that when liquid at the input side of the fixed capacity unit is under pressure said means are actuated to open said duct to short circuit the last mentioned unit to allow the centre member of the said unit and the driven member to over-run.

6. Hydraulic power transmission mechanism, as claimed in claim 1, with a duct connecting the liquid circulation system and the input of the fixed capacity unit, means whereby when the variable capacity unit has attained its minimum capacity position the ilow of liquid through the\ circulation system is stopped and the said duct is closed to prevent over-run of the driven member.

7.. Hydraulic power transmission mechanism,A as claimed in claim 1, with a duct connecting the liquid circulation system and the input of the ixed capacity unit, and means whereby said duct is closed when the capacity of the variable capacity unit is greater than that of the xed capacity unit.

8. Hydraulic power transmission mechanism, as claimed in claim 1, with a sleeve surrounding the driven member, an annular duct surrounding said sleeve, `said duct connecting the liquid circulation system and the input of the ilxed capacity unit, valve means carried' by said sleeve to control said duct, and means to operate the valve means so that said duct is opened when the capacities of the ilxed capacity unit and the variable capacity unit are equal.

9. Hydraulic power transmission mechanism, as claimed in claim'l, with a sleeve surrounding the driven lmember-and an annular duct surrounding said sleeve, 4said duct connecting the liquid circulation system and the input of the fixed capacity unit, valve means carried by said sleeve to control said duct, and means to operate the valve means whereby said duct is closed when the capacity of the variable capacity unit is less than thecapacity of the fixed capacity unit;

10. Hydraulic power transmission mechanism, as claimed in claim 1, with a sleeve surrounding the driven member and an annular duct surrounding said sleeve, said duct connecting the liquid circulation system and the input of the fixed capacity unit, valve means carried by said sleeve to control said duct, and means to operate the valve means so that said duct and the liquid circulation system are both closed when the variable unit is in the minimum capacity position.

1l. Hydraulic power transmission mechanism, as claimed in claim 1, with a sleeve surrounding the driven member and an annular duct surrounding said sleeve, said duct connecting the liquid circulation system and the input of the fixed capacity unit, valve means carried by said sleeve to control said duct and the liquid circulation system and means to operate the said valve means so that said duct and the liquid'circulation system are both closed when the variable capacity unit is in the minimum capacity position, the means to close the duct being resiliently held so that it may open when liquid at the input side of the xed capacity unit is under pressure to permit the centre gear of the iixed capacity unit and the driven member to over-run.

12. Hydraulic power transmission mechanism, as claimed in claim 1 with a sleeve surrounding the driven membel and an annular duct surrounding said sleeve, said duct connecting the liquid circulation system and the input of the fixed capacity unit, valve means and means to' operate said valve means to close the said duct when the capacity of the variablel capacity unit Iis greater than that lof the ilxed capacity unit.

13. Hydraulic power transmission mechanism, as claimed in claim 1, with a sleeve surrounding the driven member and an annular duct surrounding said sleeve, said duct connecting the liquid circulation system and Ithe input of the xed capacity unit, valve means carried by said sleeve, said valve means being arranged to close said duct and said liquid circulation system to prevent ove-run of the driven member.

14. Hydraulic power transmission mechanism, as claimed in claim 1, a liquid supply pump, two connections from said pump to the liquid circulation system and a non-return valve in each said connection, the connections being so located that liquid to make up losses will be delivered under pressure to the low pressure side of the liquid circulation system.

15.*Hydraulic power transmission mechanism, as claimed in claim 1, a leak pipe extending froml the part nearest the centre of the liquid circulation system to permit air and oil foam to be expelled when the mechanism is revolving. ALBERT WILLIAM CHAMBERLAIN.

ALAN HAWKER CHAMBERLAIN.

` HOWARD FRANCIS WINTER CHAMBERLAIN. 

